• Internally Enhanced Tubing with Enhanced Fin optimizes coil performance
• Energy Efcient PSC and 3 Phase Fan Motors with Internal Overload Protection
TM
Coil Design eliminates tube
Fans Deep
Fans Wide
1 = Inline; 2 = Double Wide
Motor
A = 1075 RPM, 3/4 HP Motor
E = ECM Motor
Design version
• Quiet ‘Swept Wing’ Fan Blade
• Fan Sections Individually Bafed with
Clean-out Panels
• Zinc Plated Huck Bolts
• Heavy Duty 24” Legs
• Double fan wide models have Two Equal
Circuits
• Control Circuit Voltage – 230 V
• Unit shipped with Nitrogen Holding Charge
• Multiple Refrigeration Circuits
• Ambient or Pressure Fan Cycling Control with
Contactor
• Johnson P66 Variable Fan Speed Control
• Efcient Variable Speed EC Motors
• Individual Fan Motor Fusing
• Non-Fused Disconnect
• Receiver with or without Heater and Insulation
OPTIONAL FEATURES
• Adjustable Flooded Head Pressure Control
(factory mounted if ordered with receiver option)
• Optional Fin Materials and Coatings
• Voltages Available for 60Hz or 50Hz
• Extended 48” Leg Kit with Cross Bracing
• Horizontal Conguration
• Optional Fin Materials
• Optional Coil Coatings
CAPACITY DATA -
T50-TCM-PDI-3
- 3 -
05/14/12
R404A
TCM60Hz
SINGLE ROW MODELS
MODEL
NUMBER
TCM009101 x 1
TCM010121 x 1
TCM011101 x 1
TCM012121 x 1
TCM01381 x 2
TCM014101 x 2
TCM016121 x 2
TCM01781 x 2
TCM018101 x 2
TCM020121 x 2
TCM02181 x 2
TCM022101 x 2
TCM024121 x 2
TCM02581 x 3
TCM028101 x 3
TCM030121 x 3
TCM03281 x 3
TCM033101 x 3
TCM035121 x 3
TCM03781 x 4
TCM039101 x 4
TCM041121 x 4
TCM04381 x 4
TCM045101 x 4
TCM048121 x 4
(1) Above capacity data based on 0oF subcooling and at sea level.
(2) TD = Condensing temperature - ambient temperature.
(3) For High Altitude applications apply the following correction factors: 0.94 for 2000 feet,
0.88 for 4000 feet and 0.81 for 6000 feet.
(4) For 50 HZ capacity multiply by 0.92. (No derate necessary when using EC motors)
R407C
R22
R507
R134a
R410A
Correction Factors for Other Refrigerants
Use
R404A
TD (Condensing dew point temperature - ambient temperature)
TCM 03482 x 2
TCM 036102 x 2
TCM 040122 x 2
TCM 04282 x 2
TCM 044102 x 2
TCM 047122 x 2
TCM 05182 x 3
TCM 056102 x 3
TCM 060122 x 3
TCM 06382 x 3
TCM 066102 x 3
TCM 070122 x 3
TCM 07382 x 4
TCM 078102 x 4
TCM 082122 x 4
TCM 08682 x 4
TCM 090102 x 4
TD (Condensing dew point temperature - ambient temperature)
10111213141516171819202122232425
(4)
R407C
R22
R507
R134a
R410A
NOTES:
(1) Above capacity data based on 0oF subcooling and at sea level.
(2) TD = Condensing temperature - ambient temperature.
(3) For High Altitude applications apply the following correction factors: 0.94 for 2000 feet,
0.88 for 4000 feet and 0.81 for 6000 feet.
(4) For 50 HZ capacity multiply by 0.92. (No derate necessary when using EC motors)
(1) Correction Factors for Other Refrigerants - Use
(2) Normal charge is the refrigerant charge for warm ambient or summer operation.
(3) 90% full is the liquid refrigerant weight at 90% of internal volume and is for reference only.
(4) For 50 Hz fan data use 60 Hz CFM (m3/h) X 0.83 (No derate necessary when using EC motors)
(5) Sound pressure level at 30 ft. (10 m)See page 13 for more data
R407C
R22
R134aR507
R410A
1.101.151.111.001.02
R404A
Values Multiplied By
GENERAL SPECIFICATIONS -
T50-TCM-PDI-3
- 7 -
05/14/12
R404A
TCM60Hz
DOUBLE ROW MODELS
MODEL
NUMBER
TCM0342
TCM0362
TCM0402
TCM0422
TCM0442
TCM0472
TCM0513
TCM0563
TCM0603
TCM0633
TCM0663
TCM0703
TCM0734
TCM0784
TCM0824
TCM0864
TCM0904
TCM0954
FANS
LONG
R404A
REFRIG. CHARGE
NORMAL
(2)
LBS
(Kg)
14.2
(6.45)56(25.39)
14.2
(6.45)56(25.39)
14.2
(6.45)56(25.39)
17.7
(8.03)72(32.61)
17.7
(8.03)72(32.61)
17.7
(8.03)72(32.61)
21.6
(9.80)85(38.59)
21.6
(9.80)85(38.59)
21.6
(9.80)85(38.59)
26.8
(12.18)
26.8
(12.18)
26.8
(12.18)
29.5
(13.39)
29.5
(13.39)
29.5
(13.39)
36.4
(16.57)
36.4
(16.57)
36.4
(16.57)
90% FULL
(3)
LBS
(Kg)
109
(49.43)
109
(49.43)
109
(49.43)
115
(52.42)
115
(52.42)
115
(52.42)
147
(66.86)
147
(66.86)
147
(66.86)
(1)
AIR FLOW
RATES
CFM
(m
28400
(48252)
27500
(46723)
26600
(45194)
27400
(46553)
26500
(45024)
25600
(43495)
42600
(72378)
41200
(69999)
39800
(67621)
41100
(69829)
39700
(67451)
38400
(65242)
56800
(96504)
55000
(93446)
53100
(90217)
54800
(93106)
53000
(90048)
51200
(86989)
SOUND
LEVEL
(5)
3
/h)
dBA
55
55
55
55
55
55
57
57
57
57
57
57
58
58
58
58
58
58
16°F to 30°F DESIGN TD10°F to 15°F DESIGN TD
INLETOUTLET
INCHES
(mm)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 5/8
(67)
2 5/8
(67)
2 5/8
(67)
2 5/8
(67)
2 5/8
(67)
2 5/8
(67)
PIPING CONNECTIONS
INCHES
(mm)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
QTY
INCHES
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
INLETOUTLET
(mm)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 5/8
(41)
1 5/8
(41)
1 5/8
(41)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
2 1/8
(54)
INCHES
(mm)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 1/8
(29)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
1 3/8
(35)
QTY
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
2
APPROX.
SHIPPING
WEIGHTS
LBS
(Kg)
830
(377)
845
(384)
860
(391)
900
(409)
920
(418)
940
(427)
1190
(541)
1210
(550)
1230
(559)
1290
(586)
1320
(600)
1350
(614)
1540
(700)
1570
(714)
1600
(727)
1670
(759)
1710
(777)
1750
(795)
(1) Correction Factors for Other Refrigerants - Use
(2) Normal charge is the refrigerant charge for warm ambient or summer operation.
(3) 90% full is the liquid refrigerant weight at 90% of internal volume and is for reference only.
(4) For 50 Hz fan data use 60 Hz CFM (m3/h) X 0.83 (No derate necessary when using EC motors)
(5) Sound pressure level at 30 ft. (10 m)See page 13 for more data
8Fan KCMCondenser with Electronically Commutated Motorvs. 8Fan
Standard Motor 1075 RPM KCM Condenser (Capacity -46 MBH/TD)
8 FAN 1075 RPM
8 FAN EC Motor
TYPICAL OPERATING
RANGE
T50-TCM-PDI-3
- 14 -
05/14/12
ABOUT EC MOTORS
EC MOTORS
60Hz
Air cooled condensers utilizing electrically commutat-
ed motor (EC motor) technology offer many benets;
Improved Efciency, Reduced Sound Levels, Speed
Control, Simplicity and Reliability
Efciency
The speed control function of an EC motor allows the
condenser to run at optimized energy levels at different operating conditions. Up to 75% in energy savings can be realized when comparing the EC motor
speed control method to a conventional fan cycling
method. See table below for power consumption and
energy savings comparisons.
Sound
As EC motor speeds vary for different operating
conditions they also offer reduced sound levels when
compared to conventional motor running full speed.
Sound levels are reduced on cooler days and in evenings. Refer to page 15 for sound ratings at different
speeds.
Head Pressure Control
EC motors make it easier to maintaining stable head
pressures when motor speeds are varied according to operating conditions. System optimization is
further enhanced compared to the system shock from
conventional cycling banks of fans off and on.
Simplicity and Reliability
The installation and control of EC motors is very
simple compared to other methods of speed control
used on conventional AC motors. Lower running operating temperatures and smooth transitional speed
changes make EC motors durable and reliable.
POWER CONSUMPTION COMPARISON
8 Fan TCM Condenser with Electronically Commutated Motor
use an EC (electronically commutated) motor / fan
combination to provide variable speed condenser
control. ECM fan/motor combinations use DC
motors with integral AC to DC conversion allowing direct connection to AC mains with the energy
saving and control benets of a DC motor. Ideally
the motors on the condenser should all be EC and
simultaneously slow down /speed up together. This
provides for maximum energy savings. However
some applications may exist where just the last fan
or pair of fans (ones closest to header) is solely EC
motors. (The remaining conventional type motors
are then cycled off by fan cycling pressure controls).
Important Warnings:
!
(Please read before handling motors)
1. When connecting the unit to the power supply,
dangerous voltages occur. Due to motor
capacitor discharge time, do not open the
motor within 5 minutes after disconnection of all
phases.
2. With a Control voltage fed in or a set speed
value being saved, the motor will restart
automatically after a power failure.
Speed adjustment Characteristics
The EC motor varies its speed linearly based on a
1-10V input signal. At 10 VDC, the motor runs at
full speed. At 0 to approx. 1 VDC, the motor turns
off. A chart of the speed control curve is shown
below. The motor can be controlled at any speed
below its nominal RPM.
Full RPM
RPM
1
Control voltage [V dc]
Control Signal
The input control signal can be supplied by an
external control signal or from a factory installed
proportional pressure control. Units with factory
installed proportional pressure controls require
no installation wiring and are adjusted with initial
factory settings. These may require further adjust-
ments to suit local eld conditions.
External Control Signal (Supplied by others)
10
3. Dangerous external voltages can be present at
terminal KL2 even when the unit is turned off.
4. The Electronics housing can get hot.
5. The cycling on and off of EC motors should be
controlled by the DC control voltage (i.e. 0V DC
will turn motor off). Excessive cycling of the
motor by line voltage contactors may cause
stress on the motors and reduce the motor life.
Contact control manufacturer for setup of external
controller to provide a 0-10 VDC control signal.
Wire the control signal to terminal board in unit
control box. See EC diagrams on pages 17-18 for
typical external signal control wiring.
TCM
T50-TCM-PDI-3
- 20 -
05/14/12
EC MOTOR APPLICA TION
EC MOTORS
60Hz
P352 Proportional Pressure Control
(Factory Installed)
Units equipped with factory installed P352 controls use a proportional plus integral pressure
controller to vary and maintain the motor speed at
the desired head pressure. The controller has two
main user adjustable features:
• Head Pressure Set point
• Throttling range
Leave the minimum Output setting at 0% and
Jumpers should be set for Direct Acting (do not
re-adjust)
Module
User Adjust
Setpoint
Potentiometer
User Adjust
Throttling Range
Potentiometer
0%
Minimum
Output
Potentiometer
LED Indicator
(Percent of Output)
THROT
RANGE
OUTPU
Connector
MIN
T
Operation Mode
Jumper Positions
34
2
1
N
O
Integration DIP Switch
Direct
Acting
Throttling range
The throttling range potentiometer controls how far
the system pressure deviates from the control set
point to generate a 100% output signal from the
control and is adjustable from 10 -100 psig. The
throttling range determines how quickly the motor
will reach full speed when detecting a change in
head pressure. For example, if the set point is 190
psig and the throttling range is 50 psig, when the
system pressure is below 190 psig, the fans will be
off. When the system pressure reaches 240 psig
(190+50) the fans will be at full speed. To make the
fans ramp more slowly the throttling range should
be increased. To maximize sound reduction and
energy efciency and to provide for the most stable
control, it is recommended this setting be left at 100
psig.
Reverse acting or direct acting mode of
operation
The reverse acting/direct acting jumper is used
to ensure the controller responds correctly to the
desired head pressure. In Direct Acting (DA) mode,
the motor speed increases as the pressure rises
above desired set point. For proper condenser
operation, this jumper MUST be in Direct Acting
(DA) mode. Failure to ensure J1 jumper is in direct
acting mode will cause the system to trip on high
head pressure.
Head Pressure Set point
The head pressure set point potentiometer is
adjustable from 90-250 psig. This maintains a
minimum condensing temp at the corresponding
pressure set point. Typical R404A set points are
from 170-200 psig. (i.e. 78°F - 89°F Cond. Temp).
Note: Very low set points may cause the fan
motors to run full speed continually even if the
condenser is properly sized. The fans will turn off
if the system pressure falls below the desired set
point.
Minimum Output
The minimum output potentiometer controls the
minimum signal sent to the motor and is factory
set at 0%. It is adjustable between 0 and 60% of
the output range. If this is adjusted to 50%, the
motors will not start running until 5V is applied
to the motor. The motor will start running at 50%
of full speed. To maximize sound reduction and
energy savings and to provide the most stable
control, it is recommended this setting be left at
0%.
Integration constant
The integration constant switch provides ability to
change controller from a proportional only control to
a proportional plus integral control. To provide the
most responsive system and to maintain a stable
head pressure, it is recommended the integration
setting be left on “fast” with the Mode switch set to
OFF (Proportional AND Integral activated)
FAST (on)
34
2
1
O
N
MEDIUM (off)
SLOW (off)
OFF (set for PROPORTIONAL /
INTEGRAL MODE)
EC MOTOR APPLICA TION
T50-TCM-PDI-3
- 21 -
05/14/12
TCM
Transducer Wiring
The P352PN controls use a P266 (P399 or P499) pressure transducer to generate a 0.5 to 4.5 VDC input signal. The
transducer is wired to the terminal block at the bottom of the control as shown in the diagram below.
EC MOTORS
60Hz
Interior View and Typical Wiring of P352PN Control
Protective Features
The EC motors have many built-in protective features.
The EC motors have functions within the motor to protect
against:
• Over-temperature of electronics
• Over-temperature of motor
• Incorrect rotor position detection
With any of these failures, the motor stops electronically
and an alarm relay is switched. With one of these failures, the motor WILL NOT automatically restart. To reset,
the power supply has to be switched off for a minimum
20 seconds once the motor is at standstill.
· Locked-rotor protection
As soon as the rotor is blocked, the motor
gets switched off electronically and the alarm
relay is switched. After de-blocking, the motor
WILL restart automatically.
· Under-voltage protection
If power supply voltage falls below ~150VAC/
3Ø (for 230V motors) or ~290VAC/3Ø (for
460V motors) for 5 seconds minimum, the
motor will be switched off electronically and
the alarm relay is switched. If power
supply voltage returns to correct values, the
motor WILL restart automatically.
· Phase Failure
If 1 phase fails for 5 seconds minimum, the
motor will be switched off electronically and
the alarm relay is switched. If all 3 phases
return to correct values, the motor WILL re
start automatically within 10-40 seconds.
EC MOTOR APPLICA TION
1LK2LK3LK
PE
T50-TCM-PDI-3
- 22 -
05/14/12
TCM
EC MOTORS
60Hz
EC Motor Wiring
All EC motor wiring is done at the factory. If any motor wiring needs to be done in the eld, the diagram below indicates
the terminal pin congurations inside the motor junction box. The terminals normally used are PE, L1, L2, L3, 0-10V/
PWM, GND, OUT 0-10V and GND. The remainder of the terminals are not normally used.
The diagram on page 17 shows typical motor wiring for a 1 x 4 EC condenser.
The condenser rst desuperheats the vapor down to its
THE BASIC REFRIGERATION CYCLE
The purpose of a refrigeration system is to absorb heat
from an area where it is not wanted and reject this heat
to an area where it is unobjectionable. By referring to the
diagram below, it can be seen that only a few components
are required to perform this task.
saturation point. This saturation point can be expressed as
the condensing temperature of the refrigerant and varies
with condenser size, load and ambient temperature.
Now the condenser must remove the latent heat of condensation from the refrigerant so that it may fully condense. After the refrigerant has fully condensed, it will be
subcooled to some extent.The liquid leaving the condenser
is still at a high pressure but at a much lower tempera-
ture and drains into the receiver. As the liquid level in the
receiver increases, the vapor is allowed to vent back up to
the condenser via \the condensate line.
Because the dip tube almost reaches the bottom of the
receiver, only liquid will enter the liquid line. This liquid now
passes through the metering device where its pressure
is reduced to the evaporating pressure. The temperature
will drop with pressure since the refrigerant will always attempt to meet its saturation point during a change of state.
High pressure/high temperature vapor leaves the compressor and is forced into the condenser via the discharge line.
GLOSSARY OF TERMS
Balance point - after a system stabilizes, the heat added
to the refrigerant during the refrigeration cycle will equal
the heat rejected at the condenser. The balance point usually refers to the actual TD that the system is operating at.
The balance point could refer to a low side balance or a
high side balance. For example, a system operating with a
120 oF (48.9 oC) condensing temperature in a 90 oF (32.2
o
C) ambient will have a condenser balance point of 30 oF
(-1.1 oC) TD.
Circuit - a circuit can be considered a group of feeds. A
condenser may be sized to handle several refrigeration
systems at one time. Each system is considered one circuit
and the number of feeds required for each circuit depends
on the THR for that particular system. Each circuit has its
own inlet and outlet header. The number of circuits on a
condenser can not exceed the total number of feeds available.
Compression Ratio - Compression ratio equals the dis-
charge pressure in pounds per square inch absolute (psia)
divided by the suction pressure in psia. The compression
ratio in a compressor increases as suction pressure decreases and as discharge pressure increases. (at sea-
level, psia is equal to psig plus 14.7).
Compressor Capacity - can be dened as the actual
refrigerating capacity available at the evaporator and suction line after considering the overall system balance point.
Compressor capacity is mainly affected by the evaporating
and condensing temperatures of the system.
The condensing temperature decreases as the
ambient temperature drops and/or as the condenser
surface increases.
the receiver. The condensate line should drop vertically
and is typically larger than the liquid line. This is to promote
free draining of the refrigerant from the condenser to the
receiver.
Condenser Temperature Difference (TD) - is the difference between the condensing temperature of the refrigerant and the temperature of the air entering the condenser.
Condensing Temperature (CT) - is the temperature
where the refrigerant vapor condenses back to a liquid.
This temperature varies with condenser size. Condensing
temperature should be kept as low as possible to maintain
higher refrigerating capacity and system efciency
Desuperheat - refers to the lowering of refrigerant super-
heat. Hot vapor entering a condenser must rst be desuperheated before any condensing of the refrigerant can
take place.
Evaporating Temperature - the temperature at which heat
is absorbed in the evaporator, at this temperature, the re-
frigerant changes from a liquid to a vapor. This evaporating
temperature is dependent on pressure and must be lower
than the surrounding temperature for heat transfer to take
place.
Feed - a single path for refrigerant ow inside a condenser.
This path begins at the inlet header and terminates at the
condenser’s outlet header. These feeds can be grouped
together to accommodate one or more circuits.
Condensate Line - (also called “Drain Leg”) is a term that
describes the refrigerant line between the condenser and
GLOSSARY OF TERMS (cont'd)
T50-TCM-PDI-3
- 30 -
05/14/12
TCM60Hz
Heat of Compression - heat is added to the refrigerant as
it is compressed. Evidence of this can be observed on the
pressure-enthalpy diagram for the refrigerant being used.
The amount of this heat is dependent on the refrigerant
type and compression ratio.
Additional heat from friction also increases the heat of
compression. All of this heat along with the heat absorbed
in the evaporator, suction line and any motor heat must be
rejected by the condenser.
Latent Heat of Vaporization (also Latent Heat of Con-
densation) - refers to the heat required to fully vaporize or
condense a refrigerant. This latent heat varies with temperature and pressure. Latent heat is often referred to as
hidden heat since adding heat to a saturated liquid or removing heat from a saturated vapor will result in a change
of state and heat content but not a change in temperature.
Liquid Line - is the piping between the receiver and the
metering device. On systems without a receiver, the liquid
line runs between the condenser and the metering device.
Open Drive - This term is given to a compressor where its
driving motor is separate from the compressor. In this type
of compressor, motor heat is not transferred to the refrigerant.
Refrigerating Effect - the total amount of heat absorbed
by the evaporator. This heat includes both latent heat and
superheat. This value is usually expressed in BTU/Hour,
(BTUH), or 1000 BTU/Hour (MBH)
Saturation - occurs whenever the refrigerant exists in both
a vapor and liquid state, example: a cylinder of refrigerant
is in a saturated condition or state of equilibrium. Any heat
removed from a saturated vapor will result in condensation.
Conversely, any heat added to a saturated liquid will result
in evaporation of the refrigerant. Temperature pressure
charts for the various refrigerants indicate saturation values. For a single component refrigerant, each temperature
value can only have one pressure when the refrigerant is
either a saturated vapor or saturated liquid. A single component refrigerant can not change state until it approaches
its saturation temperature or pressure. For refrigerant
blends, the pressure-temperature relationship is more
complex. Simply stated, Dew point temperature (saturation
point in evaporator-low side) and Bubble point temperature
(saturation point in condenser-high side) are used to dene
their saturated condition.
Subcool - to reduce a refrigerant’s temperature below its
saturation point or bubble point. Subcooling of the refrigerant is necessary in order to maintain a solid column of
liquid at the inlet to the metering device. Subcooling can
take place naturally (in the condenser) or it can be accom-
plished by a suction liquid heat exchanger or a mechanical
sub-cooler (separate refrigeration system).
Superheat - to heat a refrigerant above its saturation point
or dew point. The “amount of superheat” is the difference between the actual refrigerant temperature and its
saturation temperature. This value is usually expressed in
degrees Fahrenheit or degrees Celsius.
Total Heat of Rejection (THR) is the heat absorbed at the
evaporator plus the heat picked up in the suction line plus
the heat added to the refrigerant in the compressor. Condensers are sized according to the required THR. Compressor capacity and the heat of compression are usually
enough to determine the THR.
CONDENSER SELECTION
During a condenser selection process, the application
engineer should choose a condenser which is large
enough to reject all of the heat added to the refrigerant
during the refrigerating cycle. When the condenser is sized
to equal the total heat of rejection (THR) at design condi-
tions, enough heat will be rejected to maintain the required
condensing temperature. This will ensure that sufcient
refrigeration capacity will be maintained at the evaporator during the warm summer period when it is needed the
most.
UNDERSIZED
CONDENSER
PROPERLY SELECTED
CONDENSER
If a condenser is undersized, the condensing temperature
(CT) will be driven upwards. This naturally occurs as the
system seeks its newbalance point. As the CT increases,
the operating temperature difference (TD) of the condenser also increases. Even though the capacity of the
condenser increases with the higher TD, the refrigerating
capacity of the compressor will decrease due to the higher
condensing temperature. An undersized condenser may
perform satisfactorily when ambient temperatures are below design, but the overall system capacity will not be high
enough during the warmer periods.
Oversizing a condenser increases project costs and can
also lead to undesirable operating conditions. Low ambient control devices such as pressure regulators and fan
cycling switches operate to maintain a sufcient pressure
in the condenser during low ambient periods.On systems
utilizing a receiver and ooding type of head pressure control, more refrigerant will be required to ood the condens-
er in order to achieve the desired condensing pressure.
CONDENSER SELECTION
T50-TCM-PDI-3
- 31 -
05/14/12
TCM60Hz
Consider an air conditioning system with an oversized
condenser which is only used during the summer time
and does not have any type of head pressure control.
This particular system may experience problems due to
a lack of subcooling. Since the condenser was oversized
the amount of natural subcooling available is less. The
maximum amount of natural subcooling possible is the
difference between the condensing temperature and the
ambient temperature. If this amount of subcooling is not
enough to offset the pressure losses in the liquid line, then
ashing is certain to occur.
Flashing produces vapor at the metering device which
was designed to meter 100% liquid. One cure for this is to
apply head pressure control devices to the system that will
increase the head pressure and ensure adequate liquid
subcooling
PRELIMINARY DATA REQUIREMENTS
There are several factors that inuence the size of an
aircooled condenser. Before a condenser can be properly
selected, this information must be obtained. It may be
convenient for you to refer to the calculation worksheets as
you read through the following information.
1. What are the Desired Evaporating and Condensing
Temperatures? The evaporating temperature is needed
to determine the THR (total heat of rejection) of the condenser. As the evaporating temperature is lowered, the
heat of compression increases due to the higher compression ratio. This affects THR.
The required condensing temperature (CT) must be known
before the temperature difference can be determined. This
is necessary since condenser capacity varies with tem-
perature difference. The required compressor capacity will
determine the maximum CT since the compressor can only
provide this capacity at certain operating conditions. You
could also refer to Table 1 for CT recommendations. The
heat of compression varies with compression ratio. Both
evaporating and condensing temperatures affect the com-
pression ratio.Often customers may request a specied TD
value (i.e 10, 15 oF, (5.5 oC, 8.3 oC) etc.). The condensing
temperature is then established as being the sum of this
TD value and the design ambient temperature. (i.e 10 + 95 = 105 oF(5.5 + 35 = 40.5 oC))
2. Compressor Capacity Determine the capacity of the
compressor at the desired evaporating and condensing
conditions. Remember, tons refrigeration does not neces-
sarily equal horsepower. As the evaporating temperature
decreases and/or the condensing temperature increases,
tons refrigeration per horsepower decreases. One ton
refrigeration equals 12000 Btuh (3519W).
3. Condenser Ambient Design Temperature This will be
the maximum design temperature of the air entering the
condenser. It is typical to add about 5
outdoor design temperature in some instances to compen-
sate for radiation from a dark surface such as a black roof.
o
F to the maximum
4. Type of Compressor It is necessary to identify the
type of compressor to be utilized in the application so that
accurate heat of rejection information may be obtained.
For example, open-drive compressors can be belt driven
or direct coupled to the motor. Electrical energy from the
motor is converted to heat energy which is not transferred
to the refrigerant as in a refrigerant cooled compressor. In
a hermetic refrigerant cooled compressor, the cool suction
vapor picks up heat as it travels through the warm motor
windings. The condenser must be sized to reject this heat
along with any other heat absorbed by the refrigerant. It
can be observed in Table 2 that hermetic refrigerant cooled
compressors have higher heat of rejection factors.
5. Heat of Compression As the refrigerant is compressed
in the compressor, its heat content increases due to the
physical and thermodynamic properties of the refrigerant.
Additional heat from friction between moving parts in the
compressor also increases the heat content of the refrigerant. The amount of heat added to the refrigerant is dependent on the refrigerant type, the compression ratio and the
type of compressor.
Accurate THR or heat of compression factors may be available from the compressor manufacturer. Always attempt to
access this information prior to using other methods. If this
information is not available, refer to the heat of rejection
factors in Table 2.
However, in situations where your application exceeds the
limits of this table, such as in compound compression and
cascade systems, one of the following calculations may be
performed.
For OPEN DRIVE COMPRESSORS
Total heat of Rejection = Compressor Capacity (Btuh) + (2545 x BHP)
(KW) + (3410 x KW)
(BHP - Brake Horsepower of the motor)
For SUCTION COOLED COMPRESSORS:
Total heat Rejection = Compressor Capacity (BTUH) + (3413 x KW)
(KW may be obtained from the power input curve for that compressor)
6. What is the Refrigerant Type? A condenser’s capac-
ity can vary by 8 to 10% due to differences in physical and
thermodynamic properties. Refer to the correct refrigerant
capacity table or use factor as indicated.
7. Altitude The volume of a given mass of air increases as
it rises above sea level. As its volume increases, its density
decreases. As the air becomes less dense, its heat capacity decreases. Therefore, more air volume would have to
be forced through the condenser at 6,000 feet (1852 m)
above sea level than at sea level.
Since condenser capacities are based on operation at sea
level, an altitude correction factor must be applied to the
total heat of rejection. Basically, the load on the condenser
will be increased to a point which will compensate for the
higher altitude.
CONDENSER SELECTION
T50-TCM-PDI-3
- 32 -
05/14/12
TCM60Hz
8. Are you Replacing a Water Cooled Condenser with
a Remote Air Cooled Condenser? If this is the case,
it should be remembered that the compressor will operate at a higher discharge pressure after converting to air
cooled. To help minimize the resulting loss in capacity, the
condenser should be sized generously. In other words, you
9. Is this an application for multiple circuits? If you
wish to utilize the condenser for multiple circuits, then all
of the above data must be obtained for EACH circuit. After
obtaining this information, proceed to the MULTIPLE CIR-
CUIT WORKSHEET (for single circuit applications refer to
the SINGLE CIRCUIT WORKSHEET)
may consider keeping the balance point of the condenser
as low as possible.
TABLE 1 - CONDENSING TEMPERATURE GUIDELINES
gnitaropavE
erutarepmeT
o
04-(
o
04-(
o
01+(
2.21-(
o
53+(
o
6.1(
o
04+(
o
4(
o
9+otF
o
7.21-otC
o
43+otF
o
11.1otC
o
05+otF
o
01otC
o
05+otF
o
01otC
smetsySpmeTwoL
)spmeTpavEF
)spmeTpavEC
smetsySpmeTmuideM
o
)spmeTpavEF
)spmeTpavEC
smetsySpmeThgiH
)spmeTpavEF
)spmeTpavEC
smetsySgninoitidnoCriA
)spmeTpavEF
)spmeTpavEC
* TD - Condenser TD guideline
o
o
501ot
58ta(
o
58
F4.92(
o
001-59
F
o
8.73-53(
o
501-001
o
6.04-8.73(
o
011-501
o
3.34-6.04(
o
511-011
o
1.64-3.34(
o
)C09oF2.23(
)C
F
)C
F
)C
F
)C
F5.04ot4.92(
o
)C59oF53(o)C001oF8.73(
o
501-001
F
o
)C
6.04-8.73(
o
011-501
F
o
)C
3.34-6.04(
o
F
511-011
o
1.64-3.34(
)C
o
F
021-511
o
9.84-1.64(
)C
o
)C A)erutarepmeTtneibm
o
011-501
F
o
)C
3.34-6.04(
o
511-011
F
o
)C
1.64-3.34(
o
F
021-511
o
9.84-1.64(
)C
o
F
521-021
o
7.15-9.84(
)C
senilediuGerutarepmeTgnisnednoC
511-011
021-511
521-021
031-521
o
o
F
o
)C
1.64-3.34(
o
F
o
)C
9.84-1.64(
o
F
o
7.15-9.84(
)C
o
F
o
4.45-7.15(
)C
)C501oF6.04(
*DT
o
F
o
)C
o
021-511
F
o
)C
9.84-1.64(
o
521-021
F
o
)C
7.15-9.84(
o
F
031-521
o
4.45-7.15(
)C
o
F
531-031
o
2.75-4.45(
)C
51-01
02-51
52-02
03-52
*DT
(o)C
)3.8-6.5(
)1.11-3.8(
)9.31-1.11(
)7.61-9.31(
TABLE 2 - HEAT OF REJECTION FACTORS
ROTAROPAVE
ERUTAREPMET
o
F
04030201-
0
01
02
03
04
05
o
C
0443923281-
2171-
4
01
o
F 23(o)C001oF 83(o)C501oF 14(o)C011o34(o)C511oF 64(o)C021oF 94(o)C031oF 55(o)C041oF 06(o)C
09
MREH
NEPO
*
66.1
*
75.1
73.1
33.1
82.1
42,1
12.1
71.1
41.1
21.1
90,1
24.1
94.1
73.1
24.1
23.1
63.1
82.1
13.1
42.1
62.1
02.1
22.1
71.1
81.1
51.1
41.1
21.1
MREH
NEPO
37.1
*
26.1
44.1
35.1
93.1
64.1
43.1
04.1
03.1
43.1
62.1
92.1
22.1
52.1
81.1
12.1
61.1
71.1
31.1
MREH
NEPO
67.1
*
56.1
74.1
55.1
24.1
84.1
73.1
24.1
23.1
63.1
82.1
13.1
42.1
62.1
02.1
32.1
71.1
91.1
41.1
MREH
NEPO
08.1
86.1
85.1
05.1
44.1
83.1
33.1
82.1
42.1
02.1
NEPO
*
*
44.1
93.1
43.1
03.1
62.1
22.1
81.1
61.1
OPEN - Direct Drive or Belt Drive open compressors
HERM - Hermetic or semi-Hermetic, Refrigerant (suction) cooled motor compressors.
ERUTAREPMETGNISNEDNOC
MREH
09.1
47.1
16.1
35.1
74.1
04.1
53.1
03.1
52.1
22.1
MREH
NEPO
*
*
00.2
*
08.1
*
56.1
74.1
24.1
73.1
23.1
82.1
42.1
02.1
71.1
*
75.1
05.1
34.1
73.1
23.1
72.1
32.1
MREH
NEPO
*
*
*
*
*
*
46.1
74.1
14.1
63.1
23.1
72.1
32.1
02.1
*
65.1
94.1
34.1
73.1
13.1
62.1
MREH
NEPO
*
*
*
*
26.1
74.1
55.1
24.1
94.1
73.1
24.1
23.1
53.1
82.1
92.1
42.1
LOW AMBIENT OPERATION
T50-TCM-PDI-3
- 33 -
05/14/12
TCM60Hz
GENERAL
When a remote air cooled condenser is installed outdoors,
it will be subjected to varying temperatures. Within many
areas, winter to summer annual temperatures swings can
be as high as 120 oF (48.9 oC) or so, this will have a major
impact on the performance of the condenser. As the ambient temperature drops, the condenser capacity increases
due to the wider temperature difference between ambient
and condensing. As this happens, the condensing tem-
perature also drops as the system nds a new balance
point. Although the overall system capacity will be higher at
lower condensing temperatures, other problems can occur.
The capacity of an expansion valve is affected by both the
liquid temperature entering the valve and the pressure drop
across it. As the condensing temperature decreases, the
pressure drop across the metering device also decreases.
A lower pressure drop decreases the capacity of the valve.
Although lower liquid temperatures increase the capacity
of the metering device, the increase is not large enough to
offset the loss due to the lower pressure drop.The following three sections cover the various options used to control
condensing temperatures.
(i) Fan Cycling
Cycling of the condenser fans helps control the condensing temperature. With this approach to solving low ambient
problems, fans are taken off-line either one at a time, or in
pairs. It is not recommended that multiple fan condensers
cycle more than two fans per step. The reason for this is
that the pressure in the condenser will increase drastically
as several fans are taken off-line at the same time. This will
result in erratic operation of the refrigeration system and
applies additional stress to the condenser tubes. It is preferable to control the condensing temperature as smoothly
as possible. Fans should be cycled independently on a
condenser where the fans are all in a single row. On two
row condensers, the fans should be cycled in pairs.
Ambient temperature sensing controls can be set to bring
on certain fans when the outdoor temperature reaches a
predetermined setpoint. Pressure sensing controls are set
to bring on certain fans when the condensing pressure
reaches the setpoint on the control. Temperature or pressure setpoints and differentials should be set in such a
way as to prevent short cycling of the fans. Constant short
cycling will produce a volatile condensing pressure while
decreasing the life of the fan motors.
Fans closest to the inlet header should be permitted to run
whenever the compressor is running. If these initial fans
are wired through a cycling control, the life of the condenser may be shortened due to the additional stress placed
on the tubes and headers. Table 3 shows the fan cycling
options available for all condenser models.
(ii) Variable Motor Speed Control
If additional head pressure control is required beyond the
last step of fan cycling variable fan motor speed may be
used. Variable motor speed is optional on all condenser
models. A varying motor speed may be accomplished using
a modulating temperature or modulating pressure control. A
variable speed controller can be an electronic or solid state
device which varies the voltage going to the motor depending on the temperature or pressure of the medium being
sensed.
(iii) Refrigerant Regulating Controls
Pressure regulating controls are available from a number
of valve manufacturers. The purpose of such a control is
to regulate the refrigerant ow in such a way as to maintain a pre-selected condensing pressure. In lower ambient
temperatures, these valves throttle to maintain the desired
pressure and in doing so, ood the condenser with liquid
refrigerant.The larger the condenser surface is, the higher
its capacity will be. When a condenser is ooded, its useful
condensing surface is reduced. This is because the refrigerant occupies the space which would otherwise be used
for condensing.
Some control/check valve combinations will regulate
refrigerant ow depending on the pressure at the inlet of
the condenser.These are often referred to as inlet regulators. As the valve closes, hot gas bypasses the condenser
through a differential check valve to increase the pressure
at the receiver.
For recommended fan cycling switch settings, refer to Table
4. Differential settings on fan cycling temperature controls
should be about 5 oF (2.8 oC).On fan cycling pressure
controls, a differential of approximately 35 psig is recom-
mended. On supermarket applications condenser fans may
be cycled individually (not in pairs) and therefore lower dif-
ferential settings may apply and will depend on the specic
application.
LOW AMBIENT OPERATION
T50-TCM-PDI-3
- 34 -
05/14/12
TCM60Hz
CONDENSER
SINGLEVALVE
HEAD
PRESSURE
CONTROL
LIQUID RECEIVER
SINGLE VALVE CONDENSER PRESSURE CONTROL
(Regulates inlet pressure or outlet pressure depending on valve design)
This will ood the condenser until the condensing pressure increases to a point which will again open the valve.
Other valves regulate the refrigerant at the outlet of the
condenser to provide a similar effect. These are commonly
referred to as outlet regulators. There are also combina-
tion inlet/outlet regulators with a differential check valve or
other type of condenser bypass arrangement incorporated
within the valve.
Controls which regulate the ow of refrigerant based on
condenser inlet pressure are typically used in conjuction
with a check valve having a minimum opening differential
across the condenser. Outlet regulators typically require
a check valve with a xed pressure differential setting of
between 20 and 35 psi. The differential is needed to compensate for pressure drop through the condenser during
ooding and associated discharge piping.
Systems equipped with a condenser ooding arrange-
ment should always use a receiver having sufcient liquid
holding capacity. Additional liquid required for ooding is
only required during the winter low ambients and must be
stored somewhere in the system at the higher ambients.
Failure to use an adequately sized receiver will result in
liquid back-up in the condenser during the warmer sum-
mer months. This will cause the system to develop very
high pressures in the high side resulting in a high pressure
safety control trip.
CONDENSER
ORI
VALVE
DIFFERENTIAL
CHECK VALVE
LIQUID RECEIVER
ORI / ORD CONDENSER PRESSURE CONTROL
Determining Additional Flooded Refrigerant Charge
Additional charge will vary with the condenser design TD
and the coldest expected ambient temperature. Condensers designed for low TD applications (low temperature
evaporators) and operating in colder ambients will require
more additional charge than those designed for higher TD
applications (high temperature evaporators) and warmer
ambients.
Refer to pages 36-37 to determine the required added
refrigerant charge at the selected TD and ambient temperatures.
These charges are based on condensers using Fan
Cycling options with their last fan (Single Row Fan Models) running or last pair of fans running (Double Row Fan
models).
WARNING: Do not over charge when charging by a
sightglass. Liquid lines feeding the TXV at the evaporator
must have a solid column of liquid (no bubbles) however
bubbles at the sightglass (located adjacient to the receiver) may be normal due to the result of a higher pressure
drop at that point. Bubbles could also appear in the glass
whenever the regulating valves start to ood the condenser. Always record the number of drums or the weight of
refrigerant that has been added or removed in the system.
Overcharged systems may result in compressor failure as
well as other serious mechanical damage to the system
components.
MOTORS WITH BUILT-IN VARIABLE SPEED
ne2g
T50-TCM-PDI-3
- 35 -
05/14/12
TCM60Hz
TABLE 3 - FAN CYCLING CONTROL SCHEDULE
TABLE 4 - AMBIENT FAN CYCLING THERMOSTAT SETTINGS
nosnaFforebmuN
resnednoC
woRelgniS
sledoM
24
36
48
501
621
woRelbuoD
sledoM
ngiseD
o
.D.T
F (o)C
03)7.61(
52)9.31(
02)1.11(
51)3.8(
01)6.5(
03)7.61(
52)9.31(
02)1.11(
51)3.8(
01)6.5(
03)7.61(
52)9.31(
02)1.11(
51)3.8(
01)6.5(
03)7.61(
52)9.31(
02)1.11(
51)3.8(
01)6.5(
03)7.61(
52)9.31(
02)1.11(
51)3.8(
01)6.5(
06)6.51(
56)3.81(
07)1.12(
57)9.32(
08)7.62(
06)6.51(
56)3.81(
07)1.12(
57)9.32(
08)7.62(
06)6.51(
56)3.81(
07)1.12(
57)9.32(
08)7.62(
06)6.51(
56)3.81(
07)1.12(
57)9.32(
08)7.62(
55)8.21(
56)3.81(
07)1.12(
57)9.32(
08)7.62(
egatStse1gatSd
04)4.4(
55)8.21(
06)6.51(
56)3.81(
57)9.32(
05)0.01(
55)8.21(
56)3.81(
07)1.12(
57)9.32(
55)8.21(
06)6.51(
56)3.81(
07)1.12(
57)9.32(
05)0.01(
06)6.51(
56)3.81(
07)1.12(
57)9.32(
* NOTE: These are typical settings. Further adjustments may be necessary to suit actual eld conditions.
A thorough inspection of the equipment, including all
component parts and accessories, should be made
immediately upon delivery. Any damage caused in
transit, or missing parts, should be reported to the
carrier at once. The consignee is responsible for
making any claim for losses or damage. Electrical
characteristics should also be checked at this time to
ensure that they are correct.
LOCATION
Before handling and placing the unit into position a
review of the most suitable location must be made.
This condenser is designed for outdoor installation.
A number of factors must be taken into consideration
when selecting a location. Most important is the
provision for a supply of ambient air to the condenser,
and removal of heated air from the condenser area.
Higher condensing temperatures, decreased
performance, and the possibility of equipment failure
may result from inadequate air supply.
Other considerations include:
1. Customer requests
2. Loading capacity of the roof or oor.
3. Distance to suitable electrical supply.
4. Accessibility for maintenance.
5. Local building codes.
6. Adjacent buildings relative to noise levels.
WALLS OR OBSTRUCTIONS
All sides of the unit must be a minimum of 4 feet
(1.25 m) away from any wall or obstruction.
Overhead obstructions are not permitted. If enclosed
by three walls, the condenser must be installed as
indicated for units in a pit.
4 ft
(1.25 m)
min
UNITS IN PITS
The top of the condenser must be level with, or
above the top of the pit. In addition, a minimum of 8 feet(2.5 m) is required between the unit and the pit
walls.
MULTIPLE UNITS
A minimum of 8 feet(2.5 m) is required between
multiple units placed side by side. If placed end to end,
the minimum distance between units is 4 feet(1.25 m).
8 ft
(2.5 m)
min
LOUVERS/FENCES
Louvers/fences must have a minimum of 80% free area
and 4 feet(1.25 m) minimum clearance between the
unit and louvers/fence. Height of louver/fence must not
exceed top of unit.
8 ft
(2.5 m)
min
8 ft
(2.5 m)
min
4 ft
(1.25 m)
min
4 ft
(1.25 m)
min
INSTALLATION
T50-TCM-PDI-3
- 39 -
05/14/12
TCM60Hz
LEG INSTALLATION INSTRUCTIONS
Fig. 1
CENTRE LEG
CORNER LEG
(R.H. SIDE FACING HEADER END SHOWN)
USED ON 4 FAN MODELS ONLY
Air cooled condensers are large, heavy mechanical
equipment and must be handled as such. A fully
qualied and properly equipped crew with necessary
rigging should be engaged to set the condenser into
position. Lifting brackets or holes have been provided
at the corners for attaching lifting slings. Spreader bars
must be used when lifting so that the lifting force must
be applied vertically. See Fig. 2. Under no
circumstances should the coil headers or return
bends be used in lifting or moving the condenser.
1) Assemble centere leg as shown.
Remove two bolts from bottom ange of unit side panels
that match the hole pattern on the top anges of both legs.
Attach center legs using hardware provided at center
divider panel location.
Replace bolts that were removed from from side panels
to secure leg assembly to bottom anges of unit side panels.
2) Assemble four corner legs to bottom anges
on unit side panels and end panels using hardware
provided, at matching mounting hole patterns.
All legs are the same.
Fig. 2
Ensure the unit is placed in a level position (to ensure
proper drainage of liquid refrigerant and oil). The legs
should be securely anchored to the building structure,
sleeper or concrete pad. The weight of the condenser is
not enough to hold in place during a strong wind, the
legs must be anchored.
ANGLE BRACES
LOCATE ANGLE BRACES AS SHOWN
FOR OPTIONAL 36” and 48” LEGS.
LOCATE CROSS BRACES AS SHOWN
CROSS BRACES
ON SINGLE FAN WIDE MODELS
FOR OPTIONAL 36” and 48” LEGS.
INSTALLATION
T50-TCM-PDI-3
- 40 -
05/14/12
TCM60Hz
REFRIGERANT PIPING
All refrigeration piping must be installed by a qualied
refrigeration mechanic. The importance of correct
refrigerant pipe sizing and layout cannot be overemphasized. Failure to observe proper refrigerant
piping practices can result in equipment failure which
may not be covered under warranty.
All air cooled condensers are supplied complete with
headers and refrigerant connections sized for
connecting to standard refrigeration tubing.These
connections may not be the same as the actual line
sizes required for the eld installation. Refer to a
recognized source (ASHRAE charts, manufacturer’s
engineering manuals etc.) for line sizing.
DISCHARGE LINES
The proper design of discharge lines involves following
objective:
(1) to minimize refrigerant pressure drop, since high
pressure losses increase the required compressor
horsepower per ton of refrigeration.
bottom of a vertical riser will prevent oil (and liquid refrig-
erant) from draining back to the compressor during the
off-cycle. When the vertical lift
exceeds 30 feet (9 m), insert close-coupled traps in the
riser at 30 feet(9 m) intervals.
An alternate method of handling the oil problem would be
the addition of an oil separator see Figure 4 (b).
A reverse trap should be installed at the top of all vertical
risers. The top of the reverse trap should be the highest
point in the discharge line and should have an access
valve installed to allow the reclaimation of non-
condensible gas from the system.
Pulsation of the hot gas in the discharge line is an
inherent characteristic of systems utilizing reciprocating
compressors. The discharge line must be rigidly
supported along its entire length to prevent transmission
of vibration and movement of the line.
Discharge lines must be pitched away from the
compressor to ensure proper drainage of oil being
carried in the line. A discharge check-valve at the
CONDENSATE LINES
The condensate line must be designed to allow free
drainage of refrigerant from the condenser coil to the
receiver. Refer to Fig. 5 for typical condensate line piping
when utilizing head pressure regulating valves.
INSTALLATION
T50-TCM-PDI-3
- 41 -
05/14/12
TCM60Hz
Fig. 3 - 6
Figure 3 - Single Circuit
Figure 5 - Single circuit regulator valve
head pressure control
TYPICAL SYSTEM PIPING
Figure 4(a) - Single circuit with
double discharge riser
(may be required with
capacity control)
Figure 6 - Multiple circuits
Figure 4(b) - Single circuit with
Oil Separator (may be
All wiring and connections to the air cooled condenser
must be made in accordance with the National Electrical
Code and all local codes and regulations. Any wiring
diagrams shown are basic and do not necessarily include
electrical components which must be eld supplied. (see
pages 8-12 for typical wiring diagrams). Refer to the
Electrical Specications table on page 5 for voltage
availability and entering service requirements.
SYSTEM START-UP CHECKS
1. Check the electrical characteristics of all components
to be sure they agree with the power supply.
2. Check tightness of all fans and motor mounts.
3. Check tightness of all electrical connections.
4. Upon start-up, check fans for correct rotation. Air is
drawn through the condenser coil. To change rotation
on 3 phase units reverse any two (2) fan motor leads.
5. All system piping must be thoroughly leak checked
before a refrigerant charge is introduced.
MAINTENANCE
A semi annual inspection should be carried out by a
qualied refrigeration service mechanic. The main power
supply must be disconnected.
1. Check electrical components. Tighten any loose
connections.
2. Check control capillary tubes and lines for signs of wear
due to excessive vibration or rubbing on metal parts.
Secure if necessary.
3. Check tightness of all fans and motor mounts. Remove
any deposits which could effect fan balance. Note: Fan
motors are permanently lubricated and require only
visual inspection.
4. Clean the condenser coil using a soft brush or by
ushing with cool water or coil cleansers available
through NRP (National Refrigeration Products Inc.)
5. Update service log information (back page of service
manual)
GENERIC SERVICE PARTS
T50-TCM-PDI-3
- 42 -
05/14/12
TCM60Hz
DESCRIPTIONPart No
FAN MOTOR - 208-230-460/1/601087070
FAN MOTOR - 575/1/601087071
FAN MOTOR - 208-230/3/601088054
FAN MOTOR - 460/3/601088053
FAN MOTOR - 575/3/601087073
MOTOR MOUNT1086090
FAN BLADE - 26”, 30°1087188
FAN BLADE - 26”, 24° for use with P66 only1087213
FAN GUARD1086091
RAIN SHIELD1085266
LEGS
24”1086150
36”1086151
48”1086152
ANGLE BRACE (36” & 48” LEGS) *1086153
CROSS BRACE **1086154
* 1 Per Leg On Single Fan Wide / 2 Per Leg On Double Fan Wide
** 2 Per Unit On 1, 2 & 3 Fan Models, 3 Per Unit On 1 X 4 Fan Models (Not Req’d On Double Wide)
Finished Goods Warranty
T50-TCM-PDI-3
- 43 -
05/14/12
The terms and conditions as described below in the General Warranty Policy cover all products
manufactured by National Refrigeration.
GENERAL WARRANTY POLICY
Subject to the terms and conditions hereof, the Company warrants all Products, including Service Parts,
manufactured by the Company to be free of defects in material or workmanship, under normal use and
application for a period of one (1) year from the original date of installation, or eighteen (18) months from
the date of shipment from the Company, whichever occurs rst. Any replacement part(s) so supplied will
be warranted for the balance of the product’s original warranty. The part(s) to be replaced must be made
available in exchange for the replacement part(s) and reasonable proof of the original installation date of
the product must be presented in order to establish the effective date of the warranty, failing which, the effective date will be based upon the date of manufacture plus thirty (30) days. Any labour, material, refrigerant, transportation, freight or other charges incurred in connection with the performance of this warranty
will be the responsibility of the owner at the current rates and prices then in effect. This warranty may be
transferred to a subsequent owner of the product.
THIS WARRANTY DOES NOT COVER
(a) Damages caused by accident, abuse, negligence, misuse, riot, re, ood, or Acts of God (b) damages
caused by operating the product in a corrosive atmosphere (c) damages caused by any unauthorized
alteration or repair of the system affecting the product’s reliability or performance (d) damages caused
by improper matching or application of the product or the product’s components (e) damages caused by
failing to provide routine and proper maintenance or service to the product (f) expenses incurred for the
erecting, disconnecting, or dismantling the product (g) parts used in connection with normal maintenance,
such as lters or belts (h) products no longer at the site of the original installation (i) products installed or
operated other than in accordance with the printed instructions, with the local installation or building codes
and with good trade practices (j) products lost or stolen.
No one is authorized to change this WARRANTY or to create for or on behalf of the Company any
other obligation or liability in connection with the Product(s). There is no other representation, warranty
or condition in any respect, expressed or implied, made by or binding upon the Company other than the
above or as provided by provincial or state law and which cannot be limited or excluded by such law, nor
will we be liable in any way for incidental, consequential, or special damages however caused.
The provisions of this additional written warranty are in addition to and not a modication of or subtraction
from the statutory warranties and other rights and remedies provided by Federal, Provincial or State laws.
PROJECT INFORMATION
System
Model NumberDate of Start-Up
Serial NumberService Contractor
RefrigerantPhone
Electrical SupplyFax
“AS BUILT” SERVICE PARTS LIST
05/14/12
Service Parts List
Label
To Be Attached
HERE
NATIONAL REFRIGERATION &
AIR CONDITIONING CANADA CORP.
159 Roy Blvd.
Brantford Ontario Canada N3R 7K1
PHONE: (519) 751-0444 800-463-9517
FAX (519) 753-1140 www.t-rp.com
Due to National Refrigeration’s policy of continuous product improvement, we reserve the right to make changes without notice.
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